Fluid compressor



April 10, 1934. c. M TURSKY l FLUID COMPRESSOR Filed June f5, 1935 April10, 1934. c. M. TURSKY FLUID ACOMPRESSOR Filed June 5, 1953 3Sheets-Sheet 2 April 10, 1934. c, M. TURSKY FLUID COMPRESSOR 5sheets-sheet s Filed June 5, 1933 Patented Apr. 10, 1934 UNITED STATESPATENT OFFICE Thisinvention relates to apparatus of the generalcharacterclaimed in my application Serial No. 655,880 filed February 9, 1933,wherein a pair of axially alined pistons are reciprocated in respectivecylinders in a rotor in which the cylinders are held stationary; suchreciprocation being effected by a stationary crank. However, my presentinvention involves a substantial reversal of that arrangement in thatthe pistons are held in stationary position in the rotor, whereas thecylinders are reciprocated with respect thereto by such crank. Moreover,in said copending application, the intake of fluid to the pistons iscontrolled by valves which are carried by the reciprocatory pistons butrelatively movable therein, whereas, in the present invention, the flowof fluid to and from the cylinders is controlled by oscillation of asingle body in which the two cylinders are formed, which body has fluidpassages in its -surface for registry with vports in the rotor throughwhich the fluid flows to and from the cylinders.

- Adjunctive advantageous features of my present invention include theprovision of a single inclosing casing for both the compressor and theelectric motor by which it is driven; a fan within that casing carriedby the rotor for creating a forced draft through the casing to bothsupply the compressor with air for compression and to cool it; and thecompressed uid is further cooled by being forced to traverse thin returnbend conduits carried at the perimeter of the rotor and subjected to theair draft of the fan.

My invention includes various other novel features of yconstruction andarrangement hereinafter more definitely specified.

In said drawings, Fig. I is a" longitudinal verv tical sectional view ofa convenient embodiment of my invention.

Fig. II is a longitudinal sectional view of the rotor indicated in Fig.I, but taken in a substantially horizontal plane.

Fig. III is an elevation of the annular band which is carried at theperimeter of the rotor, as shown in Fig. I, and provided with the returnbend conduits for cooling the compressed fluid.

Fig. IV is a fragmentary' transverse sectional vView of 4saidbandand theadjacent port of the rotor with a portion of the outer casing which isconcentric therewith.

Fig. Vis a transverse sectional view of the rotor taken on the line V,V, in Fig. 1I.

Fig. VI is an elevation of the left hand end of the compressor shown inFig. I.

In said figures, the compressor is conveniently provided with the outerlcasing formedl of the,

cylindrical tube 1 having opposite end plates 2 and 3 connectedtherewith by tap bolts 5 and 6, said plates 2 and 3 having feet 7 and 8with holes for fastening means by which the compressor may be secured instationary position.

Said plates 2 and 3 have axially alined bearings 10 and 11 and saidbearing 10 holds the stationary axial shaft 12 which is secured thereinconveniently by the nut 13 engaging the screw thread 14 on said shaftexterior to said bear- 65 ing 10.

As indicated in Fig. VI, said bearing 10 has suction and discharge ports15 and 16 respectively at opposite sides thereof with which respectiveconduits 17 and 18 may be connected exterior to 70 said casing, todirect the iiow of uid to and from the latter. Said ports 15 and 16 arerespectively in communication with the passageways 20 and 21 which areformed in coaxial relation with said stationary shaft 12 conveniently asindicated in Fig. I. Said passageways 20 and 21 are respectivelyprovided with ports 22 and 23 extending transversely through the wall ofsaid shaft 12 to the exterior thereof, as indicated in Fig. I.

The rotor 25 has the tubular shaft 26 journaled on said stationary shaft12, as indicated in Fig. I, and has the shaft 27 at its opposite end incoaxial relation with said shaft 26 and journaled in the casing bearing11, as shown in Fig. I.

As shown in Figs. II and V, said rotor 25 has a pair of axially spacedand alined pistons 29 and 30 xed at their outer ends at the perimeter ofsaid rotor, conveniently by annular flanges 31 and 32 which are pushtted in corresponding seats in said rotor from which they may, however,be withdrawn for repairs by screw devices then temporarily engaged withsockets 34 and 35 in said pistons. The cylinder 37, shown in Figs. I,II, and V, has recesses 38 and 39 at its opposite ends in coaxialrelation, `fitted to said pistons 29 and 30, and has the crank bearing40 intermediate of said recesses for thel crank 41 by which saidcylinder is caused to reciprocate and oscillate upon. its axis in saidrotor as a consequence of the rotation of the latter.

Said crank 41- has at its outer end the ball member 42 fitted in theballsocket bearing 43` which is held stationary by the nut 45 on the 47and 48 in said rotor, by oscillation of said cylinder; whereby rotationof said rotor effects reciprocation and oscillation of said cylinder 37and controls the passage of fluid toand from said recesses 38 and 39 atthe inner ends of said pistons 29 and 30.

Said fluid inlet passageway 20 in said stationary shaft 12 is incommunication with said fluid inlet passageways 47 in the rotor, throughthe annular chamber 52, surrounding said shaft 12 within the rotor shaft26, and the drilled holes 53, 54, and

55 in the rotor. Similarly, the fluid outlet passageway 21 in thestationary shaft 12 is in communication with the fluid outletpassageways 48 in said rotor 25 through the annular chamber 57surrounding said shaft 12 and the drilled holes 58, 59, 60, and 61,shown at the lower part of Fig. I. Said holes 60 and 61 are connected bythe return bend conduits 62. There are six of said conduits 62 arrangedin a circular series at the perimeter of the rotor, as indicated inFigs. III and IV, and but two of the drilled openings 61, as indicatedin Fig. V. However, said return bend conduits 62 are connected aroundthe circumference of said rotor 25 by channels 64 extending spirally inthe circumference of said rotor, as indicated in Fig. III. As indicatedin Figs. I and IV, I find it convenient to mount said return bendconduits 62 in the annular band 65 which fits the circumference of saidrotor 25 and is held upon the latter by the annular flanges 66 and 67 ofthe bearing members respectively carry- I ing the shafts 26 and 27 andwhich are rigidly connected with said rotor by cap screws 68 indicatedin Figs. I and V. The effect of the arrangement above described is Lsuchthat the compressed iluid discharged from the cylinder recesses 38 and39 by the reciprocation of the cylinder is forced through thepassageways 48 and drilled holes 61 and caused to traverse the entirecircumference of the rotor through the channels 64 and return bendconduits 62 so as to be cooled by exchange of heat with the atmospherearound said rotor through the side walls of said return bends 62. Suchcooling effect is enhanced by the disposition of said return bends 62obliquely with respect to the axis of the rotor 25, as shown in Fig.III, so that they serve as fan blades to force the circulation of airthrough the compressor casing. Moreover, such circulation is augmentedby providing said rotor 25 with the fan comprising the blades 70, shownin Fig. I, With the effect of minimizing the temperature of thecompressor and the fluid compressed thereby.

Although said rotor 25 and its appurtenances may be rotated by anyconvenient means; I find it convenient to provide the rotor shaft 26with the armature 71 in cooperative relation with the stationary field72 which is conveniently-fixed in the casing 1, by bolts 74 and nuts 75indicated in Fig. I. Said field 72 is conveniently energized by theelectric coils 76 which are operatively connected with a source ofcurrent exterior to said casing by way of the cable 77 shown in Fig. I.

As indicated in Fig. I, I prefer to interpose the bronze bushing 78between said stationary shaft 12 and the rotor shaft 26, said bushingbeing held stationary in the shaft 26 by the nut 79 and bearing axiallyupon the steel thrust washer 80 in said bearing 10. In order tocompensate for wear and prevent endwise movement and consequent noise ofsaid rotor, I also prefer to interpose the bronze bushing.81 betweensaid stationary shaft 12 and said rotor shaft 26 with the spring 82constantly stressing said bushing 81 toward the annular flange 46 onsaid shaft 12. Said spring extends in the sealing chamber 52 surroundingthe joint between said shaft 12 and the rotary compressor shaft 26 andhas at its opposite ends abutment washers 83 and abutment rings 84. Saidrings 84 are ground to fit the contiguous surfaces of the bushings 78and 81 and hold elastic packing material 84', whereby said joint isnormally rendered airtight to prevent direct communication between saidair inlet port 15 and air outlet port 16 around said stationary shaftl2. However, said chamber 52 serves as a by-pass from the outletpassageway 58 to the inlet passageway 53 for any compressed fluid whichmay leak past said seal, and thus accumulation of detrimental fluidpressures is prevented.

Moreover, I find it convenient'to lubricate said shafts and bushings byforming the oil chamber 85 in the bearing 10 on said casing which ismaintained charged with oil 86 through the oil inlet 87 and to encirclesaid bushing 78 with the loose ring 88 which dips into said oil andcauses it to flow through the oil inlets 89 in said bushing 78 tolubricate the surface of the latter which is in contact with saidstationary shaft l2. The oil thus supplied to the surface of saidstationary shaft l2 finds its way between said rings 84 and bushings 78and 81 and into the annular grooves 90 in the bronze bushing 81 andthence through the oil hole 91, shown in Fig. I, to. the surface of theball 42 which is gyrated in the stationary socket bearing 43, by therotation of the rotor 25. The drilled hole 92 extending axially throughsaid crank 41 is in communication with said oil hole 91 and with the oilchamber 93 in said rotor 25, as shown in Fig. I, and effects thedelivery of oil to the surface of the cylinder 37 which oscillates andreciprocates in said rotor 25. The axial opening 94 in said rotor ismerely an air vent for said chamber 93 to permit reciprocation of saidcrank 41 transversely to the axis of said cylinder 37, incident to theoscillation of the latter, without compressing the air in said chamber93.

I also find it convenient to provide said bearing 11 with the oilchamber 95 charged with oil 96 through the oil inlet 97 and to encirclethe bushing 98 with the loose ring 99 which dips into said oil andcauses it to flow through the oil inlet 100 in said bushing 98 tolubricate the surface of the latter which is in contact with the rotorshaft 27.

In order to eliminate dust from the atmospheric air or other fluid whichmay b e compressed in the structure above described, I prefer to providethe compressor casing with screens 101 and 102 covering the openings inthe opposite ends of said casings. Said screens are preferably made ofwire cloth of a mesh much finer than indicated in the drawings. l

Said compressor operates as follows: The stationary field 72 beingenergized through the cable 77 shown in Fig. I, the armature 71 isrotated, carrying with it the tubular shaft 26 and rotor 25 with theeffect of reciprocating the cylinder 37 with respect to the pistons 29and 30 which are fixed in said rotor 25, as shown in Fig. 1I. Suchreciprocation draws air alternately into the piston chambers which arerecesses 38 and 39 in said cylinder 37, through the inlet conduit 17 andsuction port v15 indicated in Fig. VI, passageway 20 and inlet port 22,shown at thel left hand end of Fig. I, and through the intake chamber52, and drilled holes 53, 54, and 55 shown in the upper part of Fig. I.Such reciprocation also alternately expels the compressed air from saidpiston chambers through the drilled holes 61, return bend conduits 62,drilled holes 60, 59, and 58, shown at the lower portion of Fig. I, intothe annular chamber 57 shown in Fig. I, and thence out through the port23 and axial passageway 21 in the shaft 12 to the discharge port 16indicated at the left hand end of Fig. VI, which port is incommunication with the discharge conduit 18 shown at the left hand sideof Fig. VI. As above noted, said return bends 62 and the fan blade 70carried by said rotor 25 forcibly circulate the atmospheric air throughthe compressor casing screens 101 and 102 with the effect of cooling thearmature coil 'l1 and field coil 72 and the return bends 62 so that theheat of compression of the air in said piston chambers is dissipatedthrough said return bends 62 as the compressed air is on its Way to saiddischarge port 16.

However, I do not desire to limit myself tol the precise details ofconstruction and arrangement herein set forth, as it is obvious thatvarious modiiications may be made therein without departing from theessential features of my invention, as defined in the appended claims.

I claim: f

1. In a fluid compressor, the combination with a rotor; of a pair ofaxially spaced and alined pistons fixed at their outer ends at theperimeter of said rotor; a cylinder having recesses at its respectivelyopposite ends, in coaxial relation, fitted to said pistons and having acrank bearing intermediate of said recesses; said cylinder being mountedto reciprocate and oscillate upon its axis in said rotor; a crank fittedto said bearing and having at its outer end a ball member; a bearingfitted to said ball member having means to hold said bearing stationary;fluid inlet and outlet passageways in said rotor; fluid ports in saidcylinder respectively in communication with the recesses therein andadapted to be alternately registered with said inlet and outletpassageways by oscillation of said cylinder; whereby,rotationof saidrotor effects reciprocation and oscillation of said cylinder andcontrols the passage of fluid to and from said recesses at the innerends of said pistons.

2. A structure as in claim 1, including a circular series of return bendconduits at the perimeter of said rotor in communication with the fluidpassageways in said rotor; whereby rotation of said rotor is effectiveto cool the fluid during its traverse of said return bends by exchangeof heat through the walls of said conduits to the atmosphere surroundingsaid rotor.

3. A structure as in claim 1, including a circular series of return bendconduits at the perimeter of said rotor in communication with the fluidpassagewaysf in said rotor; each of said conduits being similarlyinclined to the axis of said rotor to form fan blades; whereby rotationof said rotor forces the air to traverse the outer surface of saidconduits and is effective to cool the uid during its traverse of saidreturn bends by exchange of heat through the walls of said conduits tothe atmosphere surrounding said rotor. l

4. In a fluid compressor, the combination with an outer casing havingopenings at each end for circulation of air therethrough and bearings atits opposite ends which are axially alined; of a shaft having means forholding it stationary in one of said bearings; a rotor having a tubularshaft at one end journaled on said stationary shaft, and having a shaftat its opposite end, in coaxial relation therewith, journaled in theother of said casing bearings; a pair of axially spaced and alinedpistons extending in diametrical relation with said rotor and fixed attheir outer ends at the perimeter of said rotor; a cylinder havingrecesses at its respectively opposite ends, in coaxial relation, iittedto said pistons and having a crank bearing intermediate of saidrecesses; said cylinder being mounted to reciprocate and oscillate uponsaid pistons; a crank fitted to said cylinder bearing and having at itsouter end a ball member; a ball socket bearing fitted to said ballmember; means for holding said socket bearing stationary on saidstationary shaft; fluid inlet and outlet passageways in said rotor;fluid ports in said cylinder respectively in communication with therecesses therein and adapted to be alternately registered with saidinlet and outlet passageways by oscillation of said cylinder; whereby,rotation of said rotor effects reciprocation -and oscillation of saidcylinder and controls the passage of iluid to and from said recesses atthe inner ends of said pistons.

5. A structure as in claim 4, having ud suction and discharge ports insaid casing bearing which supports said stationary shaft, and havingfluid passageways in said stationary shaft in coaxial relation inrespective communication with said ports and with the passageways insaid rotor.

6. A structure as in claim 4, including a cirof said rotor incommunication with the fluid passageways in said rotor; each of saidconduits being inclined to the axis of said rotor to form a fan blade;whereby rotation of said rotor forces the air in said casing to traversethe outer surface of said conduits and is effective to cool the fluidduring its traverse of said return bends by exchange of heat through thewalls of said conduits to the atmosphere surrounding said rotor.

CHARLES M. TURSKY.

